Turbo compressor and turbo refrigerator

ABSTRACT

A turbo compressor according to the present invention supports a rotational shaft fixed to an impeller by a bearing in a freely rotatable manner, and supplies the lubricant oil to a plurality of sliding portions that are slid due to the rotation of the rotational shaft. Furthermore, the turbo compressor includes a oil supply nozzle in which a first injection hole, which injects the lubricant oil toward a predetermined first fueling place among a plurality of sliding portions to be supplied with the lubricant oil, and a second injection hole, which injects the lubricant oil toward a second fueling place different from the first fueling place, are provided. According to the present invention, it is possible to provide a turbo compressor capable of reducing the labor and the costs of manufacturing and a turbo refrigerator including the same.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a turbo compressor and a turborefrigerator. Priority is claimed on Japanese Patent Application No.2010-51930, filed Mar. 9, 2010, the content of which is incorporatedherein by reference.

2. Description of Related Art

As a refrigerator that cools or refrigerates a cooling object such aswater, there is known a turbo refrigerator including a turbo compressorwhich compresses and discharges a refrigerant by the rotation of animpeller. For example, as disclosed in Japanese Patent Application,First publication No. 2007-177695, the turbo compressor included in theturbo refrigerator includes a motor generating rotational power, animpeller to which the rotational power of the motor is transmitted andwhich rotates, and a pair of gears that transmits the rotational powerof the motor to the impeller. The impeller and one of the gears areprovided on a rotational shaft, and the rotational shaft is supported bya bearing in a freely rotatable manner.

Incidentally, in the aforementioned turbo compressor, a lubricant oilsupply structure is provided which supplies lubricant oil for thelubricant and the cooling to a sliding portion such as a bearing or anengagement portion of a pair of gears. The lubricant oil supplystructure includes a supply pump which delivers the lubricant oil, aplurality of nozzles that are respectively provided near the bearing orthe engagement portion of the pair of gears, and inject the lubricantoil to the sliding portions, and supply pipes that respectively connecteach nozzle with the supply pump.

However, since the plurality of nozzles are used, the number ofcomponents constituting the lubricant oil supply structure increase andthe assembly thereof requires much labor, whereby the labor and thecosts for manufacturing the turbo compressor increase.

The present invention was made in view of the above problems, and anobject thereof is to provide a turbo compressor capable of reducing thelabor and the costs of manufacturing and a turbo refrigerator includingthe same.

SUMMARY OF THE INVENTION

In order to solve the above problems, the present invention adopts thefollowing means:

In the turbo compressor according to the present invention, a rotationalshaft fixed to an impeller is supported by a bearing in a freelyrotatable manner, and the lubricant oil is supplied to a plurality ofsliding portions that are slid due to the rotation of the rotationalshaft. Furthermore, the turbo compressor includes an oil supply nozzlein which a first injection hole, which injects the lubricant oil towarda predetermined first fueling place among a plurality of slidingportions to be supplied with the lubricant oil, and a second injectionhole, which injects the lubricant oil toward a second fueling placedifferent from the first fueling place, are provided.

In the present invention, since the oil supply nozzle can supply theplurality of sliding portions with the lubricant oil, it is needless torespectively provide nozzles for supplying the lubricant oil near theplurality of sliding portions. Furthermore, the number of supply pipesor the like to be connected to the nozzles are also reduced by the useof the oil supply nozzle of the present invention. Thus, the number ofnozzles or supply pipes for supplying the plurality of sliding portionswith the lubricant oil is reduced.

Furthermore, it is preferable that the turbo compressor according to thepresent invention includes a driving portion that generates therotational power, and a pair of gears that transmits the rotationalpower of the driving portion to the rotational shaft; and the firstfueling place is a bearing, and the second fueling place is anengagement portion of the pair of gears.

Furthermore, in the turbo compressor according to the present invention,it is preferable that a rolling bearing is used as the bearing and thefirst fueling place is an inner ring of the rolling bearing.

Furthermore, in the turbo compressor according to the present invention,it is preferable that the oil supply nozzle includes a first planeorthogonal to the extension direction of the first injection hole, and asecond plane orthogonal to the extension direction of the secondinjection hole, the first injection hole is opened to the first plane,and the second injection hole is opened to the second plane.

Furthermore, a turbo refrigerator according to the present inventionincludes a condenser that cools and liquefies a compressed refrigerant,an evaporator that evaporates the liquefied refrigerant and removesvaporization heat from a cooling object to cool the cooling object, anda compressor that compresses the refrigerant evaporated by theevaporator and supplies the refrigerant to the condenser, and, as thecompressor, any one of the aforementioned turbo compressors is employed.

According to the present invention, it is possible to reduce the numberof nozzles, the supply pipes or the like for supplying the plurality ofsliding portions with the lubricant oil. For that reason, it is possibleto reduce the labor and the costs of manufacturing in the turbocompressor and the turbo refrigerator including the same.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a block diagram that shows a schematic configuration of aturbo refrigerator in an embodiment of the present invention.

FIG. 2 is a horizontal cross-sectional view of a turbo compressor in anembodiment of the present invention.

FIG. 3 is a cross-sectional view taken along line A-A of FIG. 2.

FIG. 4 is a cross-sectional view taken along line B-B of FIG. 3.

FIG. 5 is an enlarged plan view of a spur gear and a pinion gear whichare included in a turbo compressor in an embodiment of the presentinvention.

FIG. 6A is a vertical cross-sectional view that schematically shows aoil supply nozzle in an embodiment of the present invention.

FIG. 6B is a bottom view that schematically shows a oil supply nozzle inan embodiment of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

Hereinafter, an embodiment of the present invention will be describedwith reference to FIGS. 1 to 6B. In addition, in the respective drawingsused in the following description, in order to make the respectivemembers realizable sizes, the scales of the respective members aresuitably changed.

FIG. 1 is a block diagram that shows a schematic configuration of aturbo refrigerator S1 in the present embodiment. The turbo refrigeratorS1 in the present embodiment is installed in a building, a factory orthe like, for example, in order to create cooling water forair-conditioning. As shown in FIG. 1, the turbo refrigerator S1 includesa condenser 1, an economizer 2, an evaporator 3, and a turbo compressor4.

The condenser 1 is supplied with a compressed refrigerant gas X1 whichis a refrigerant in a compressed gas state, and converts the compressedrefrigerant gas X1 into a refrigerant liquid X2 by a coolingliquefaction. As shown in FIG. 1, the condenser 1 is connected to theturbo compressor 4 via a flow path R1 through which the compressedrefrigerant gas X1 flows, and is connected to the economizer 2 via aflow path R2 through which a refrigerant liquid X2 flows. In addition,in the flow path R2, an expansion valve 5 for decompressing therefrigerant liquid X2 is installed.

The economizer 2 temporarily stores the refrigerant liquid X2 that wasdecompressed by the expansion valve 5. The economizer 2 is connected tothe evaporator 3 via a flow path R3 through which the refrigerant liquidX2 flows, and is connected to the turbo compressor 4 via a flow path R4through which a gaseous phase component X3 of the refrigerant generatedby the economizer 2 flows. In addition, in the flow path R3, anexpansion valve 6 for further decompressing the refrigerant liquid X2 isinstalled. Moreover, the flow path R4 is connected to the turbocompressor 4 so as to supply a second compression stage 22 describedlater included in the turbo compressor 4 with the gaseous phasecomponent X3.

The evaporator 3 evaporates the refrigerant liquid X2 and cools acooling object by removing the vaporization heat from the cooling objectsuch as water. The evaporator 3 is connected to the turbo compressor 4via a flow path R5 through which a refrigerant gas X4 generated by theevaporation of the refrigerant liquid X2 flows. In addition, flow pathR5 is connected to a first compression state 21, described later,included in the turbo compressor 4.

The turbo compressor 4 compresses the refrigerant gas X4 and convertsthe same into the compressed refrigerant gas X1. The turbo compressor 4is connected to the condenser 1 via the flow path R1 through which thecompressed refrigerant gas X1 flows as mentioned above, and is connectedto the evaporator 3 via the flow path R5 through which the refrigerantgas X4 flows.

In the turbo refrigerant S1 configured as above, the compressedrefrigerant gas X1 supplied to the evaporator 1 via the flow path R1 isliquefied and cooled by the evaporator 1 and becomes the refrigerantliquid X2.

The refrigerant liquid X2 is decompressed by the expansion valve 5 whenbeing supplied to the economizer 2 via the flow path R2 and istemporarily stored in the economizer 2 in the decompressed state, andthen, the refrigerant liquid X2 is further decompressed by the expansionvalve 6 when being supplied to the evaporator 3 via the flow path R3 andis supplied to the evaporator 3 in the further decompressed state.

The refrigerant liquid X2 supplied to the evaporator 3 is evaporated bythe evaporator 3, becomes the refrigerant gas X4, and is supplied to theturbo compressor 4 via the flow path R5.

The refrigerant liquid X4 supplied to the turbo compressor 4 iscompressed by the turbo compressor 4, becomes the compressed refrigerantgas X1, and is supplied to the condenser 1 via the flow path R1 again.

In addition, the gaseous phase component X3 of the refrigerant generatedwhen the refrigerant liquid X2 is stored in the economizer 2 is suppliedto the turbo compressor 4 via the flow path R4, is compressed togetherwith the refrigerant gas X4, and is supplied to the condenser 1 via theflow path R1 as the compressed refrigerant gas X1.

Moreover, in the turbo refrigerator S1, when the refrigerant liquid X2is evaporated in the evaporator 3, the cooling or the refrigeration ofthe cooling object is performed by removing the vaporization heat fromthe cooling object.

Next, the turbo compressor 4, which is a characteristic portion of thepresent embodiment, will be described in more detail.

FIG. 2 is a horizontal cross-sectional view of the turbo compressor 4 inthe present embodiment. FIG. 3 is a cross-sectional view taken from lineA-A of FIG. 2. FIG. 4 is a cross-sectional view taken from line B-B ofFIG. 3. Furthermore, FIG. 5 is an enlarged plan view of a spur gear 31and a pinion gear 32 included in the turbo compressor 4 in the presentembodiment. Moreover, FIGS. 6A and 6B are schematic views of an oilsupply nozzle 35 in the present embodiment, FIG. 6A is a verticalcross-sectional view of the oil supply nozzle 35, and FIG. 6B is abottom view of the oil supply nozzle 35. In addition, all of the spurgear 31, the pinion gear 32 and a gear casing 33 in FIG. 4 and the oilsupply nozzle 35 in FIG. 5 are indicated by imaginary lines.

As shown in FIG. 2, the turbo compressor 4 in the present embodimentincludes a motor unit 10, a compressor unit 20, and a gear unit 30.

The motor unit 10 includes a motor 12 (a driving portion) which has anoutput shaft 11 and becomes a driving source for driving the compressorunit 20, and a motor casing 13 which surrounds the motor 12 and in whichthe motor 12 is installed. In addition, the driving force, which drivesthe compressor unit 20, is not limited to the motor 12, but may be, forexample, an internal combustion engine.

The output shaft 11 of the motor 12 is supported by a first bearing 14and a second bearing motor 15 fixed to the motor casing 13 in a freelyrotatable manner.

The compressor unit 20 includes a first compression stage 21 which takesin and compresses the refrigerant gas X4 (see FIG. 1), and a secondcompression stage 22 which further compresses the refrigerant gas X4compressed in the first compression stage 21 and discharges the same asthe compressed refrigerant gas X1 (see FIG. 1).

As shown in FIG. 3, the first compression stage 21 includes a firstimpeller 21 a (an impeller) which gives velocity energy to therefrigerant gas X4 to be supplied from a thrust direction and dischargesthe same in a radial direction, a first diffuser 21 b which compressesthe refrigerant gas X4 by converting the velocity energy given to therefrigerant gas X4 by the first impeller 21 a into pressure energy, afirst scroll chamber 21 c which leads the refrigerant gas X4 compressedby the first diffuser 21 b to the outside of the first compression stage21, and an inlet port 21 d which takes in the refrigerant gas X4 andsupplies the same to the first impeller 21 a.

In addition, a part of the first diffuser 21 b, the first scroll chamber21 c and the inlet port 21 d is formed by a first impeller casing 21 ethat surrounds the first impeller 21 a.

In the compressor unit 20, a rotational shaft 23 extending over thefirst compression stage 21 and the second compression stage 22 isprovided. The first impeller 21 a is fixed to the rotational shaft 23and is rotated by the transmission of the rotational power of the motor12 (see FIG. 2) to the rotational shaft 23.

Furthermore, in the inlet port 21 d of the first compression stage 21, aplurality of inlet guide vanes 21 f for adjusting the inlet capacity ofthe first compression stage 21 are installed. The respective inlet guidevanes 21 f are freely rotatable so that an exterior area from a flowdirection of the refrigerant gas X4 can be changed by the drivingmechanism 21 g fixed to the first impeller casing 21 e. Furthermore, atthe outside of the first impeller casing 21 e, a vane driving portion 24(see FIG. 2) is installed which is connected to the driving mechanism 21g to rotate the respective inlet guide vanes 21 f.

The second compression stage 22 includes a second impeller 22 a (animpeller) that gives velocity energy to the refrigerant gas X4, which iscompressed in the first compression stage 21 and then is supplied from athrust direction, and discharges the refrigerant gas X4 in a radialdirection, a second diffuser 22 b which compresses the refrigerant gasX4 by converting the velocity energy given to the refrigerant gas X4 bythe second impeller 22 a into pressure energy and discharges therefrigerant gas X4 as the compressed refrigerant gas X1, a second scrollchamber 22 c which leads the compression refrigerant gas X1 dischargedfrom the second diffuser 22 b to the outside of the second compressionstage 22, and an introduction scroll chamber 22 d which leads therefrigerant gas X4 compressed in the first compression stage 21 to thesecond impeller 22 a.

In addition, a part of the second diffuser 22 b, the second scrollchamber 22 c and the introduction scroll chamber 22 d is formed by asecond impeller casing 22 e that surrounds the second impeller 22 a.

The second impeller 22 a is fixed to the rotational shaft 23 so that arear surface thereof faces the first impeller 21 a, and is rotated bythe transmission of the rotational power of the motor 12 to therotational shaft 23.

The second scroll chamber 22 c is connected to the flow path R1 (seeFIG. 1) for supplying the condenser 1 with the compressed refrigerantgas X1 and supplies the flow path R1 with the compressed refrigerant gasX1 led from the second compression stage 22.

In addition, the first scroll chamber 21 c of the first compressionstage 21 and the introduction scroll chamber 22 d of the secondcompression stage 22 are connected to each other via an external piping(not shown) which is provided separately from the first compressionstage 21 and the second compression stage 22, and the refrigerant gas X4compressed in the first compression stage 21 via the external piping issupplied to the second compression stage 22. The above-mentioned flowpath R4 (see FIG. 1) is connected to the external piping, and thegaseous phase component X3 of the refrigerant generated in theeconomizer 2 is supplied to the second compression stage 22 via anexternal piping.

The rotational shaft 23 is supported by a third bearing 26 in freelyrotatable manner, which is fixed to the second impeller casing 22 e in aspace 25 between the first compression stage 21 and the secondcompression stage 22, and a fourth bearing 27 (bearing) which is fixedto an end portion of a casing protruding portion 22 f protruding fromthe second impeller casing 22 e to the gear unit 30 side. In therotational shaft 23, a labyrinth seal 23 a for suppressing the flow ofthe refrigerant gas X4 from the introduction scroll seal 22 d to thegear unit 30 side is provided.

Furthermore, as shown in FIG. 2, the gear unit 30 includes a spur gear31 (gear) which is fixed to the output shaft 11, a pinion gear 32 (gear)which is fixed to the rotational shaft 23 and is engaged with the spurgear 31, and a gear casing which accommodates the spur gear 31 and thepinion gear 32, and transmits the rotational power of the output shaft11 of the motor 12 to the rotational shaft 23. In addition, the gearunit 30 includes a lubricant oil supply portion 34 for supplying thelubricant oil to a plurality of sliding portions which slides due to therotation of the rotational shaft 23.

An outer diameter of the spur gear 31 is greater than that of the piniongear 32, and the rotational power of the motor 12 is transmitted to therotational shaft 23 so that the revolution of the rotation shaft 23increases relative to that of the output shaft 11 by the cooperationbetween the spur gear 31 and the pinion gear 32. In addition, at thetime the rotational power of the motor 12 is transmitted to therotational shaft 23, the diameters of the plurality of gears may be setso that the revolution of the rotational shaft 23 is identical to thatof the output shaft 11 or reduces without being limited to thetransmission method.

The gear casing 33 is molded separately from the motor casing 13 and thesecond impeller casing 22 e and connects them to each other. In an innerpart of the gear casing 33, an accommodation space 33 a foraccommodating the spur gear 31, the pinion gear 32 and the lubricant oilsupply portion 34 is formed. The gear casing 33 and the second impellercasing 22 e are fixed to each other using a plurality of bolts 33 b.Furthermore, in the gear casing 33, an oil tank 33 c is provided inwhich the lubricant oil to be supplied to the sliding portion of theturbo compressor 4 is collected and stored.

The lubricant oil supply portion 34 supplies the lubricant oil for thelubrication and the cooling to the fourth bearing 27, which is a slidingportion accompanied by the rotation of the output shaft 11 and therotational shaft 23, and an engagement portion 38 (see FIG. 4) betweenthe spur gear 31 and the pinion gear 32. The lubricant oil supplyportion 34 includes a oil supply nozzle 35 which injects and suppliesthe lubricant oil to the plurality of sliding portions, and a supplypipe 36 which is connected to the oil supply nozzle 35 and supplies thelubricant oil.

The supply tube 36 is connected to the supply pump 37 delivering thelubricant oil stored in the oil tank 33 c, via a supply flow path (notshown) provided outside the gear casing 33. The supply pump 37 isinstalled on an external surface of the oil tank 33 c.

In addition, another supply portion may be provided which supplies thelubricant oil not only to the lubricant oil supply portion 34 but alsoto other sliding portions (for example, the first bearing 14).

As shown in FIG. 3, the oil supply nozzle 35 is provided on the upperside of the pinion gear 32 and is fixed to the casing protruding portion22 f of the second compression stage 22. In addition, in the casingprotruding portion 22 f, an oil discharging port 22 g is formed which issituated at the lower part side of the pinion gear 32 to discharge thelubricant oil supplied from the oil supply nozzle 35.

Furthermore, the oil supply nozzle 35 includes a hole portion 35 aconnected to the supply pipe 36 extending in a vertical direction, afirst injection hole 35 b and a second injection hole 35 c whichcommunicate with the hole portion 35 a and are opened toward the outside(with regard to the second injection hole 35 c, see FIG. 4).

The first injection hole 35 b is opened toward the fourth bearing 27which is set as a first supply place among a plurality of slidingportions to be supplied with the lubricant oil. In addition, the fourthbearing 27 is a so-called rolling bearing, includes an inner ring 27 a,an outer ring 27 b, and a plurality of rolling bodies 27 c disposedbetween the inner ring 27 a and the outer ring 27 b, and the firstinjection hole 35 b is opened toward the inner ring 27 a. That is, morespecifically, the above-mentioned first supply place is the inner ring27 a of the fourth bearing 27.

Since the first injection hole 35 b is opened toward the fourth bearing27, the lubricant oil can be supplied from the first injection hole 35 bto the fourth bearing 27, which can lubricate and cool the fourthbearing 27. Furthermore, since the first injection hole 35 b is openedtoward the inner ring 27 a, it is possible to actively lubricate andcool the inner ring 27 a having a large heating value due to thesliding.

As shown in FIG. 4, the second injection hole 35 c is opened to theengagement portion 38 between the spur gear 31 and the pinion gear 32,which is a second supply place among the plurality of sliding portionsto be supplied with the lubricant oil. For that reason, the lubricantoil can be injected and supplied from the second injection hole 35 c tothe engagement portion 38, which can lubricate and cool the spur gear 31and the pinion gear 32 in the engagement portion 38.

In addition, an end side of the supply pipe 35 is connected to the holeportion 35 a of the oil supply nozzle 35 and the other end side thereofis connected to the inner surface of the gear casing 33.

Furthermore, as shown in FIG. 5, the second injection hole 35 c isopened toward the center portion in a width direction (left and rightdirection in FIG. 5) of the engagement portion 38. For that reason, itis possible to effectively spread the lubricant oil over the widthdirection of the engagement portion 38. In addition, the openingdirection of the first injection hole 35 b may be suitably tilted to acircumferential direction of the inner ring 27 a so as to follow therotational direction of the rotational shaft 23.

As mentioned above, the oil supply nozzle 35 includes the firstinjection hole 35 b and the second injection hole 35 c. As a result, itis possible to supply the lubricant oil to any one of the fourth bearing27 and the engagement portion 38 slid along with the rotation of theoutput shaft 11 and the rotational shaft 23 by a single oil supplynozzle 35. For that reason, in the present embodiment, there is needlessto provide nozzles for supplying the lubricant oil near the fourthbearing 27 and the engagement portion 38, respectively, and the numberof supply pipes or the like to be connected to the nozzle alsodecreases. Thus, it is possible to reduce the number of nozzles, thesupply pipes or the like for supplying the lubricant oil to the fourthbearing 27 and the engagement portion 38, which can reduce the labor andthe costs of manufacturing in the turbo compressor 4.

As shown in FIGS. 6A and 6B, the first injection hole 35 b and thesecond injection hole 35 c of the oil supply nozzle 35 connect the frontend side (a lower part side of FIG. 6A) of the oil supply nozzle 35 tothe inner peripheral surface of the hole portion 35 a formed of acylindrical shape. Furthermore, the extension direction of the firstinjection hole 35 b and the second injection hole 35 c is tiltedrelative to the extension direction of the hole portion 35 a at apredetermined angle. In addition, as shown in FIG. 6B, the firstinjection hole 35 b and the second injection hole 35 c branch off in aradial direction around the axis of the hole portion 35 a.

Furthermore, the oil supply nozzle 35 includes a first plane 35 dorthogonal to the extension direction of the first injection hole 35 b,and a second plane 35 e orthogonal to the extension direction of thesecond injection hole 35 c. The first injection hole 35 b is opened tothe first plane 35 d and the second injection hole 35 c is opened to thesecond plan 35 e. As a result, the first plane 35 d and the second plane35 e are tilted to the proximal end side with respect to the front endsurface (a lower end surface in FIG. 6A) of the oil supply nozzle 35 ata predetermined angle and form a slope surface facing the fourth bearing27 or the engagement portion 38.

At the time of the production of the oil supply nozzle 35, the main bodyof the oil supply nozzle 35 and the hole portion 35 a are formed by themechanical working (a cutting working and a drill working). Next, afterthe first plane 35 d and the second plane 35 e are formed by themechanical working (the cutting working and the drill working), thefirst injection hole 35 b and the second injection hole 35 c are formedby the mechanical working (the drill working).

Next, the operation of the turbo compressor 4 in the present embodimentwill be described.

Firstly, the rotational power of the motor 12 is transmitted to therotational shaft 23 via the spur gear 31 and the pinion gear 32, wherebythe first impeller 21 a and the second impeller 22 a of the compressorunit 20 are rotated.

When the first impeller 21 a is rotated, the inlet port 21 d of thefirst compression stage 21 enters a negative pressure state, and therefrigerant gas X4 flows from the flow path R5 into the firstcompression stage 21 via the inlet port 21 d.

The refrigerant gas X4 flowed into the inner portion of the firstcompression stage 21 flows into the first impeller 21 a in the thrustdirection. This refrigerant gas X4 is provided with the velocity energyby the first impeller 21 a, and is discharged in the radial direction.

The refrigerant gas X4 discharged from the first impeller 21 a iscompressed by converting the velocity energy to the pressure energy bythe first diffuser 21 b.

The refrigerant gas X4 discharged from the first diffuser 21 b is led tothe outside of the first compression stage 21 via the first scrollchamber 21 c.

Moreover, the refrigerant gas X4 led to the outside of the firstcompression stage 21 is supplied to the second compression stage 22 viaan external piping (not shown).

The refrigerant gas X4 supplied to the second compression stage 22 flowsinto the second impeller 22 a via the introduction scroll chamber 22 din the thrust direction. This refrigerant gas X4 is provided with thevelocity energy by the second impeller 22 a, and is discharged in theradial direction.

The refrigerant gas X4 discharged from the second impeller 22 a isfurther compressed by converting the velocity energy into the pressureenergy by the second diffuser 22 b and becomes the compressedrefrigerant gas X1.

The compression refrigerant gas X1 discharged from the second diffuse 22b is led to the outside of the second compression stage 22 via thesecond scroll chamber 22 c.

The compressed refrigerant gas X1 led to the outside of the secondcompression stage 22 is supplied to the condenser 1 via the flow pathR1.

Furthermore, the turbo compressor 4 in the present embodiment includesthe above-mentioned lubricant oil supply portion 34. For that reason, itis possible to supply the lubricant oil to any one of the fourth bearing27 and the engagement portion 38 slid due to the output shaft 11 and therotational shaft 23, thereby performing the lubrication and the cooling.

As mentioned above, the operation of the turbo compressor 4 is finished.

According to the present embodiment, since the same oil supply nozzle 35supplies the fourth bearing 27 and the engagement portion 38 with thelubricant oil, it is possible to reduce the number of nozzles, supplypipes or the like for supplying oil to the member. As a result, in theturbo compressor 4 and the turbo refrigerator S1, it is possible toobtain an effect capable of reducing the labor and the costs ofmanufacturing.

Furthermore, since the structure of the oil supply nozzle 35 is simpleand the oil supply nozzle 35 can be produced by a simple mechanicalworking, the effect can be further improved.

In addition, the first injection hole 35 b and the second injection hole35 c are titled toward the front end side in the extension direction ofthe hole portion 35 a at a predetermined angle, and branch off aroundthe axis of the hole portion 35 a in the radial direction. For thatreason, the lubricant oil supplied from the supply pipe 36 toward thefront end side of the hole portion 35 a is powerfully injected from thefirst injection hole 35 b and the second injection hole 35 c which aretitled toward the front end side and branch off, with the result that itis possible to effectively lubricate and cool the fourth bearing 27 andthe engagement portion 38. Furthermore, since the first injection hole35 b and the second injection hole 35 c are opened vertically to thefirst plane 35 d and the second plane 35 e facing the fourth bearing 27or the engagement portion 38, it is difficult for the lubricant oilinjected from the first injection hole 35 b and the second injectionhole 35 c to be adversely affected by the first plane 35 d and thesecond plane 35 e.

As mentioned above, although a preferable embodiment according to thepresent invention has been described with reference to the drawings, itis needless to say that the present invention is not limited to therelated art. Overall shapes, combinations or the like of the respectivemembers shown in the aforementioned example are examples, and can bevariously changed in a scope of not departing from the gist of thepresent invention based on the design request or the like.

For example, although the oil supply nozzle 35 in the above-mentionedembodiment supplies the fourth bearings 27 and the engagement portion 38with the lubricant toil, the oil supply nozzle may be a nozzle whichsupplies a plurality of other sliding portions with the lubricant oilwithout being limited thereto. Furthermore, although the oil supplynozzle 35 includes the first injection hole 35 b and the secondinjection hole 35 c, the oil supply nozzle 35 may have a configurationincluding, for example, three or more injection holes.

Furthermore, although the turbo compressor 4 in the above embodiment isa two-stage compression type of turbo compressor including the firstcompression stage 21 and the second compression stage 22, the turbocompressor may be a single-stage compression type or a multi-stage typeof three stages or more without being limited thereto. Furthermore,although the turbo compressor 4 in the above embodiment is used in theturbo refrigerator S1, for example, the turbo compressor 4 may be used,for example, as a supercharger that supplies an internal combustionengine with the compressed air.

1. A turbo compressor which supports a rotational shaft to be fixed toan impeller by a bearing in a freely rotatable manner, and supplies alubricant oil to a plurality of sliding portions that are slid due tothe rotation of the rotational shaft, the compressor comprising: a oilsupply nozzle in which a first injection hole, which injects thelubricant oil toward a predetermined first fueling place among aplurality of sliding portions to be supplied with the lubricant oil, anda second injection hole, which injects the lubricant oil toward a secondfueling place different from the first fueling place, are provided. 2.The turbo compressor according to claim 1, further comprising: a drivingportion that generates a rotational power, and a pair of gears thattransmits the rotational power of the driving portion to the rotationalshaft, wherein the first fueling place is the bearing, and the secondfueling place is an engagement portion of the pair of gears.
 3. Theturbo compressor according to claim 2, wherein a rolling bearing is usedas the bearing, and the first fueling place is an inner ring of therolling bearing.
 4. The turbo compressor according to claim 1, whereinthe oil supply nozzle includes a first plane orthogonal to the extensiondirection of the first injection hole, and a second plane orthogonal tothe extension direction of the second injection hole, the firstinjection hole is opened to the first plane, and the second injectionhole is opened to the second plane.
 5. The turbo compressor according toclaim 2, wherein the oil supply nozzle includes a first plane orthogonalto the extension direction of the first injection hole, and a secondplane orthogonal to the extension direction of the second injectionhole, the first injection hole is opened to the first plane, and thesecond injection hole is opened to the second plane.
 6. The turbocompressor according to claim 3, wherein the oil supply nozzle includesa first plane orthogonal to the extension direction of the firstinjection hole, and a second plane orthogonal to the extension directionof the second injection hole, the first injection hole is opened to thefirst plane, and the second injection hole is opened to the secondplane.
 7. A turbo refrigerator according to the present invention whichincludes a condenser that cools and liquefies a compressed refrigerant,an evaporator that evaporates the liquefied refrigerant and removesvaporization heat from a cooling object to cool the cooling object, anda compressor that compresses the refrigerant evaporated by theevaporator and supplies the condenser with the refrigerant, wherein theturbo compressor according to claim 1 is employed as the compressor. 8.A turbo refrigerator according to the present invention which includes acondenser that cools and liquefies a compressed refrigerant, anevaporator that evaporates the liquefied refrigerant and removesvaporization heat from a cooling object to cool the cooling object, anda compressor that compresses the refrigerant evaporated by theevaporator and supplies the condenser with the refrigerant, wherein theturbo compressor according to claim 2 is employed as the compressor. 9.A turbo refrigerator according to the present invention which includes acondenser that cools and liquefies a compressed refrigerant, anevaporator that evaporates the liquefied refrigerant and removesvaporization heat from a cooling object to cool the cooling object, anda compressor that compresses the refrigerant evaporated by theevaporator and supplies the condenser with the refrigerant, wherein theturbo compressor according to claim 3 is employed as the compressor. 10.A turbo refrigerator according to the present invention which includes acondenser that cools and liquefies a compressed refrigerant, anevaporator that evaporates the liquefied refrigerant and removesvaporization heat from a cooling object to cool the cooling object, anda compressor that compresses the refrigerant evaporated by theevaporator and supplies the condenser with the refrigerant, wherein theturbo compressor according to claim 4 is employed as the compressor. 11.A turbo refrigerator according to the present invention which includes acondenser that cools and liquefies a compressed refrigerant, anevaporator that evaporates the liquefied refrigerant and removesvaporization heat from a cooling object to cool the cooling object, anda compressor that compresses the refrigerant evaporated by theevaporator and supplies the condenser with the refrigerant, wherein theturbo compressor according to claim 5 is employed as the compressor. 12.A turbo refrigerator according to the present invention which includes acondenser that cools and liquefies a compressed refrigerant, anevaporator that evaporates the liquefied refrigerant and removesvaporization heat from a cooling object to cool the cooling object, anda compressor that compresses the refrigerant evaporated by theevaporator and supplies the condenser with the refrigerant, wherein theturbo compressor according to claim 6 is employed as the compressor.